System and method for a multiphase hydrocarbon pump having an auger coupling

ABSTRACT

A bladeless conical radial rotary machine method and system are disclosed. Turbo-machinery and methods are disclosed for a bladeless conical radial rotary machine wherein fluid is directed axially within the pump body to produce an axial output. The rotor comprises a plurality of spaced apart conical elements. The fluid is smoothly directed to any number of subsequent boundary layer pumping stages which are axially positioned with respect to each other. The fluid is smoothly directed to any number of subsequent boundary layer pumping stages which are axially positioned with respect to each other. A coupling between pumping stages is disclosed.

CROSS-REFERENCE TO RELATED APPLICATIONS

This patent application is related to U.S. Pat. No. 7,192,244 entitledBladeless Conical Radial Rotary Machine and Method by Salvatore Grande,III et al., issued Mar. 20, 2007 and also U.S. patent application Ser.No. 62/307,097 filed on Mar. 11, 2016 entitled System and Method For ATurbomachine Multiphase Hyrdrocarbon Pump, Motor And Fluid Separator bySalvatore Grande, III et al., also U.S. patent application Ser. No.62/369,316 filed on Aug. 1, 2016 entitled A System and Method for anAuger Coupling by Salvatore Grande, III et al., all of which are herebyincorporated by reference in their entirety.

BACKGROUND OF THE INVENTION

Boundary layer or bladeless rotary machines, pumps, and other relatedturbo-machinery have been known and patented as early as May 6, 1913when Nikola Tesla described a boundary layer pump in U.S. Pat. No.1,061,142. The boundary layer pump taught in that patent utilizesrotating flat disks which have no blades, vanes, or propellers, so thatsuch pumps are now also referred to as bladeless pumps. In related U.S.Pat. No. 1,061,206, Tesla disclosed a fluid driven boundary layer orbladeless rotary machine which may be utilized as a prime mover, such asa hydro-electric power generator for transforming kinetic energy inflowing fluids into electrical energy. Another example of relatedboundary layer or bladeless turbo-machinery invented by Tesla, anddescribed in U.S. Pat. No. 1,329,559, shows a boundary layer orbladeless rotary machine implemented as an internal combustion enginewherein one or more combustion chambers may be substantiallycontinuously fed with fuel and air to thereby produce expanding hotgases which drive the rotary machine.

FIELD OF THE INVENTION

The present invention relates to an auger coupling between pumps, pumpsections and boundary layer pumps and in particular to an auger couplingused between a pump and a turbomachine used as a motor, pump and filterin the production of hydrocarbons.

SUMMARY OF THE INVENTION

A system and method are disclosed for an auger coupling between pumps.The pumps can be auger pumps, reciprocating pumps and turbomachine pumpsthat pumps and filters hydrocarbons. The turbomachine pump acts as afilter that separates fluid from solids. A system and method aredisclosed that places the auger coupling between pumps that pump andcompresses hydrocarbons. A system and method are disclosed that placesthe auger pumps between pump sections that pump fluid to a turbomachineto generate rotation and acts as a hydraulic motor downhole. In anotherillustrative embodiment of the invention the turbo machine is rotated ona motor shaft to generate horse power to reduce a horsepower requiredfrom the motor turning the motor shaft. In another illustrativeembodiment of the invention a system and method are disclosed for aturbomachine that pumps and filters hydrocarbons. The filter separatesfluid from solids. A system and method are disclosed that pumps andcompresses hydrocarbons. A system and method are disclosed that pumpsfluid to a turbomachine to generate rotation and acts as a hydraulicmotor downhole.

BRIEF DESCRIPTION OF THE FIGURES

FIG. 1 is an elevational view, in section, showing two stages of aboundary layer turbine pump in accord with one possible embodiment ofthe present invention;

FIG. 2 is an enlarged view of a single stage boundary layer turbine pumpin accord with one possible embodiment of the present invention;

FIG. 3 is a side view of an illustrative embodiment;

FIG. 4 is a side view of an illustrative embodiment;

FIG. 5 is a side view of an illustrative embodiment;

FIG. 6 is a side view of an illustrative embodiment;

FIG. 7 is a side view of an illustrative embodiment;

FIG. 8 is a plan view of an illustrative embodiment;

FIGS. 9A and 9B are sectional views of an illustrative embodiment havingan auger coupling between sections;

FIG. 10 is a cross sectional view of an illustrative embodiment of anauger coupling;

FIG. 11 is a cross sectional view of an illustrative embodiment of anauger coupling placed between pump sections; and

FIGS. 12A, 12B, 13 and 14 are cross section views of illustrativeembodiment of an auger coupling placed between pump sections using aturbomachine to generate horsepower.

The figures are exemplary only and not intended to limit the scope ofthe invention.

DETAILED DESCRIPTION

A bladeless rotary machine method and apparatus are disclosed. The terms“bladeless rotary machine”, “rotary machine” and “turbomachine” are usedsynonymously herein to indicate a machine that transfers energy betweena rotor and a fluid, including turbines, compressors and motors. Inparticular, illustrative embodiments, turbomachinery and methods aredisclosed for a bladeless rotary machine wherein fluid is directedaxially within the body. In different illustrative embodiments, thebladeless rotary machine is used as both a motor and/or apump/compressor. When used as a pump, a bladeless rotary machine bodyreceives fluid, wherein fluid is directed axially within the pump bodyto produce an axial output. When used as a compressor, a bladelessrotary machine body receives fluid as gas wherein fluid is directedaxially within the pump body to produce an axial output. When used as amotor, fluid passing in a reverse direction relative to the pump output,is forced through the rotary machine body to produce kinetic rotationalenergy to impart rotational energy to drive another equipment attachedto bladeless rotary machine. The bladeless rotary machine includes butis not limited to a rotor that includes but is not limited to aplurality of axially-spaced apart rotor elements. In a particularembodiment, the rotor elements are disks. In another embodiment, thebladeless rotary machine body includes but is not limited to a rotorthat includes but is not limited to a plurality of spaced apart rotorelements that in one illustrative embodiment are conical elements.

In one particular embodiment, a bladeless rotary machine is disclosedthat creates a vortex for discharge that facilitates downhole fluidseparation. The nature of the vortex allows the centrifugal force tonaturally separate the fluids where the heavier particles are moved tothe outer wall of the vortex and lighter fluids, including but notlimited to a gas is moved to the inner wall of the vortex toward acentral drive shaft. In a downhole environment, wherein the turbomachineis submerged in a subterranean hole (also referred to herein as a“wellbore” drilled in the earth for the recovery of hydrocarbons), portsare provided to separate solids and heavier particles from a fluidpumped by the turbomachine and thus substantially removes solids fromthe fluid. The remaining fluids after the solids are removed is producesor transported to the surface of the Earth as a liquid and gas. In anillustrative embodiment, the heavier particles (i.e., solids) are portedfrom the outer perimeter of a vortex of fluid formed by the spinningturbomachine rotor and returned down hole. The lighter fluid and gas areported from the center of the vortex and transported (pumped) through awellbore or pipeline to the surface. In a pipeline environment, heavierparticles are separated and ported from a fluid pumped in the pipeline.In one embodiment, the solids are ported back down the well bore.

In an illustrative embodiment, the turbomachine is provided as a fluidseparator (also referred to herein as a “filter”) to provide cleaned-upmultiphase fluid wherein the turbomachine substantially removes solidsand heavier particles from the multiphase fluid by creating a spinningvortex multiphase fluid created by the spinning turbomachine rotor. Themultiphase fluid contains gas, liquid and solids. In another embodiment,the turbomachine is provided as a fluid separator, wherein fluid andsolids are separately ported from the vortex before the multiphase fluidis pumped by another centrifugal pump, which can be a conventional pumpin capable of efficiently pumping multiphase fluid containing solids andliquid. Removing the solids (also referred to herein as “particles”)from the multiphase fluids in the turbomachine, to create “cleaned up”fluid, enables use of standard pumps that can pump the cleaned-up fluidbut would suffer inefficiencies such as deterioration from impingementif the standard pump pumping the multiphase fluid containing solidsbefore it is processed by the turbomachine to produce cleaned-up fluid.

In another embodiment, the bladeless rotary machine is a multi-stagecompressor with no pistons or blades which increases the reliabilityover a standard type gas compressor. In another embodiment, thebladeless rotary machine is used as a multi-stage compressor to increasegas yield in a downhole environment, wherein downhole gas is compresseddownhole by the bladeless rotary machine and compressed gas pumped uphole, where the gas is stored in a compressed state, eliminating a needfor a gas compressing station on the surface. In an illustrativeembodiment, the compressor increases the pressure of the gas and thusincreases the density and amount gas being pumped. In anotherembodiment, the bladeless rotary machine is used as a multi-stagecompressor that is used in pipelines to boost flow. In anotherembodiment, the bladeless rotary machine is used as a multi-stage pumpthat is used in pipelines to boost flow. In another illustrativeembodiment the bladeless rotary machine is used as a jet engine which isless subject to wear and damage than a blade rotary machine fromimpingement of foreign objects from sand, birds, etc. The multi-stagebladeless rotary machine is substantially more resistant to damage fromimpingement of foreign objects from sand, birds, etc.

In another illustrative embodiment, the bladeless rotary machine is asewage pump. The bladeless rotary machine sewage pump can pump largersolids than a normal centrifugal pump can handle. In anotherillustrative embodiment, the bladeless rotary machine is an injectionpump. High pressure pumping from surface to deep downhole being able tohandle pressure changes, cavitation and solids. In another illustrativeembodiment, the bladeless rotary machine is a multi-stage generator. Inanother illustrative embodiment, the bladeless rotary machine any rotarymachine application.

In another illustrative embodiment, the bladeless rotary machine is acoal pump. In another illustrative embodiment, the bladeless rotarymachine is a multi-stage coal pump that substantially increases adistance that the coal solids and slurry can be pumped. In anotherillustrative embodiment, the bladeless rotary machine is a gravel pump.In another illustrative embodiment, the bladeless rotary machine is amulti-stage steam pump. The multi-stage steam pump is multi-staged andtherefore enables using a smaller in diameter pump than a single stagerotary machine.

In another illustrative embodiment, the bladeless rotary machine is amining dewatering pump. The bladeless rotary machine used for miningdewatering carries heavy and abrasive particles with substantially lesswear and impingement. In another illustrative embodiment, the bladelessrotary machine is used for in situ mining wherein an acid solution isapplied to mine tailings. The acid leaches metal from the tailing oreand car recover much more the heavy metal (e.g., copper or gold). Thisis a very acidic and abrasive solution to pump into the plating processand the bladeless rotary machine handles with substantially less wearand impingement.

In another illustrative embodiment, the bladeless rotary machine is usedfor substantially silent ship propulsion wherein cavitation issubstantially reduced due to the non-propeller design for propelling aship.

In another illustrative embodiment, the bladeless rotary machine is usedas a hydraulic motor that can be used to drive other equipment.Introducing hydraulic fluid into the turbomachine in an oppositedirection from the pump output, that is pumping fluid into theturbomachine's output, causes the bladeless rotary machine to perform asa hydraulic motor. In another embodiment, the turbomachine hydraulicmotor drives drill bits, pumps and compressors in a reduced diameterslim hole environment.

In another illustrative embodiment, the bladeless rotary machine motoris used to provide high pressure drilling mud to a drill bit. In anotherillustrative embodiment, the bladeless rotary machine is used to removedrill cuttings that are associated with a drilling process which arehighly abrasive and in a slurry condition.

In an embodiment, the spacing between the rotor elements in theturbomachine, which can be disks and conical elements, is dynamicallyadjustable to accommodate efficiently moving or pumping varying densityfluids moving through the bladeless rotary machine when used as a pump.The spacing between the disks or conical elements is adjusted toaccommodate efficiently generating rotational kinetic energy as a motorgenerated from moving varying density fluids moving through thebladeless rotary machine when used as a motor. When used as a pump, theconical elements and disk elements rotate to impart acceleration of aworking fluid through the spaces between the disks or conical elementsusing boundary layer adhesion techniques. The working fluid, which canbe a liquid, a gas or a liquid containing solids, is smoothly directedto any number of subsequent boundary layer pumping or motor stages whichare axially positioned with respect to each other. The working fluid istypically a multiphase fluid containing liquid, gas and solids. Forlower density fluids, such as gas having a low fluid density (FD), theaxial distance (d) between the rotor elements, (e.g., conical and diskelements) is adjusted to be smaller than a distance d between theconical and disk elements when a heavier fluid is passing through therotary machine.

In another illustrative embodiment, the bladeless rotary machine pump isequipped with a dynamically length adjustable shaft element wherein anaxial distance between adjacent rotor elements on the dynamically lengthadjustable shaft is adjustable so that the characteristics of thebladeless rotary machine pump are adjustable for differentcharacteristics of the multiphase fluid being pumped. When adjacentrotor elements are farther apart, the flow path between the adjacentrotor elements is wider. The wider flow paths between adjacentturbomachine rotor elements can more efficiently handle higher densityfluids and multiphase fluids containing solids than narrower flow pathsthat are provided between the rotor elements when the adjacentturbomachine rotor elements are closer together. In another particularillustrative embodiment, the density of the multiphase (fluids, fluidsbearing solids, solids and gas) being pumped is monitored and thedistance between the adjacent rotor elements, e.g., disks is adjusted toaccommodate the density of the medium being pumped to increase theefficiency of the bladeless rotary machine pump. In another illustrativeembodiment, the axial distance between the adjacent rotor elements isadjusted so that a first distance between the disks is greater forhigher density mediums such as multiphase fluids containing solids. Inanother illustrative embodiment, the distance between the adjacent rotorelements is adjusted to a second distance so that the distance betweenthe disks is less than the first distance for higher density mediumssuch as fluids. In another illustrative embodiment, the distance betweenthe disks is adjusted to a third distance so that the axial distancebetween the disks is less than the first and second distances for lowerdensity mediums such as gas. In another illustrative embodiment, eachdistance axial distance between beach disk and conical element isindividually adjustable.

In another illustrative embodiment, a turbomachine motor is provided andequipped with a dynamically length adjustable shaft wherein the distancebetween adjacent rotor elements on a dynamically length adjustable shaftin the turbomachine motor are adjustable so that the characteristics ofthe bladeless rotary machine motor are adjustable for differentcharacteristics of the medium being used to drive the bladeless rotarymachine as a motor. In another particular illustrative embodiment, thefluid density (FD) of the medium (multiphase fluids, liquids, fluidsbearing solids, solids and gas) being supplied to the turbomachine motoris monitored and the distance between the adjacent rotor elements isadjusted to accommodate the fluid density of the medium being suppliedto the turbomachine motor to increase the efficiency of the turbomachinemotor. In another illustrative embodiment, the distance between theadjacent rotor elements is adjusted so that a first distance between theadjacent rotor elements is greater for higher density mediums such asmultiphase fluids containing solids. In another illustrative embodiment,the distance between the disks is adjusted to a second distance so thatthe distance between the adjacent rotor elements is less than the firstdistance for lower density mediums such as gas, fluids in liquid formand fluids substantially not containing solids. In another illustrativeembodiment, the distance between the disks is adjusted to a thirddistance so that the distance between the disks is less than the firstand second distances for lower density mediums such as gas.

In another illustrative embodiment, a bladeless rotary machine is usedboth as a motor and as a pump downhole. In another illustrativeembodiment, two bladeless rotary machines are provided on a drill stringdownhole, a first bladeless rotary machine is used as a motor downholeand a second bladeless rotary machine is used as a pump downhole. Inanother illustrative embodiment, two bladeless rotary machines areprovided on a drill string downhole, a first bladeless rotary machine isused as a motor downhole and a second bladeless rotary machine is usedas a pump with a solids port for returning solids downhole.

Fluid Density (FD) is inversely proportion to the American PetroleumInstitute (API) gravity. API gravity is a scale expressing the gravityor density of liquid petroleum products. The measuring scale iscalibrated in terms of degrees API; it is calculated as follows:Degrees API=(141.5/(sp. gr. 60° F./60° F.))−131.5The higher the API gravity, the lighter the compound. Light crudesgenerally exceed 38 degrees API and heavy crudes are commonly labeled asall crudes with an API gravity of 22 degrees or below. Intermediatecrudes fall in the range of 22 degrees to 38 degrees API gravity.

One of the major problems associated with oil and gas production is thelarge volume of produced water. Operators around the world are facingsignificant costs with the treatment and disposal of produced water.Downhole separation, has been developed to reduce the costs of producedwater and increase oil production. Downhole separation is the techniquewhere oil and gas from the produced water is separated at the bottom ofthe well and reinject a portion of the produced water into anotherformation, while the oil and gas are pumped to the surface. Thereduction in cost can attributed to the downhole treatment of theproduced water since most of the topside produced water treatmentfacilities are reduced in number. Since most of the produced water doesnot reach the surface this creates an added value of minimizing theopportunity for contamination of underground sources of drinking waterthrough leaks in casing and tubing during the injection process.

One illustrative embodiment of the present invention discloses abladeless rotary machine as it applies to fluid pumping problems.However, it will be understood that general mechanical structuresutilized in the bladeless conical radial rotary machine of the presentinvention may be implemented in various types of turbo-machinery and thepresent invention is not intended to be limited to a particular type ofrotary machine implementation.

Unlike more traditional pumps which utilize vanes, blades, augurs,buckets, pistons, gears, diaphragms, and the like, boundary layer pumps,such as those described by Tesla, may typically utilize multiplerotating parallel flat disks. Bladeless or boundary layer pumps operateto pump fluids by utilizing the fluid properties of adhesion andviscosity. These fluid properties create an interaction between thefluid and the rotating flat disks of the boundary layer or bladelesspump whereby the mechanical energy of the rotating rotary machine may beimparted to the fluid to induce the fluid to flow through the pumphousing.

Boundary layer pumps, also referred to herein as “turbomachines” havebeen reported to have some significant advantages over the moretraditional pumps especially when utilized for pumping fluids other thancool, clean, homogenous liquids. The vanes, buckets, or the like, oftraditional pumps wear and lose effectiveness due to normal frictionand/or impingement with particles such as sand or other abrasives.However, the flat surfaces of boundary layer pumps are much lesssusceptible to wear and may have little or no wear even after extendeduse. Boundary layer pumps have been found to be especially effective forpumping high viscosity fluids wherein the efficiency of such pumps mayincrease as the fluid viscosity increases. Boundary layer pumps havealso been reported to be more cost effective in terms of reliability anddecreased downtime for pumping problematic multiphase fluids, which maycomprise gases, liquids, and/or solid materials. Boundary layer pumpshave been found to greatly reduce maintenance costs and downtime whenused to replace more traditional pumps. Moreover, the tolerances of theflat disks for boundary layer pumps tend to be much looser than thoserequired for operation of more traditional pumps thereby resulting inhigher reliability. Traditional centrifugal pumps rely on narrowinternal clearances with close tolerances to maintain the pressure inthe pump needed for maximum efficiency. These tolerances may wear awayquickly in abrasive fluid pumping service so that these traditionaldesign pumps steadily lose efficiency and eventually fail. Traditionalpump manufacturers sometimes make more income from replacementcomponents due to wear and failure from operating in a harsh pumpingenvironment than on the sales of original pumps.

Due to the absence of spinning blades or impellers, boundary layer pumpsare more gentle on sensitive fluids pumped e.g. shear-sensitive fluids.As an example, boundary layer pumps have been found to pump watercontaining live fish without banning the fish. Other problems related totraditional axial, centrifugal, and mixed flow pumps include problemsrelating to cavitation. Cavitation describes a vacuum-like condition inthe pump which can occur when liquid in the low-pressure area of thepump vaporizes. Vapor bubbles implode as they pass to regions of highpressure and can create a shock wave powerful enough to lift metal offthe pump. The energy required to accelerate the liquid to high velocityand fill the void left by the bubbles causes a drop-in capacity. In aboundary layer pump, because the fluid flow changes are kept as gradualas possible, with laminar flow rather than turbulent flow, the risk ofcavitation is greatly reduced.

As discussed briefly above, impingement damage is produced by solidswhich engage the vanes of a pump and erode it. The higher the angle ofimpingement between the particle and the vane, the greater the damage,with a ninety-degree impingement angle being the most damaging.Traditional pumps are sometimes operated at lower speeds to reduceimpingement wear, but lower speeds result in lower fluid flow and lowerhorsepower. In a boundary layer pump, with smooth disks, the impingementdamage is substantially reduced or substantially eliminated due tolaminar flow over the disks with a substantially zero-degree impingementangle. Boundary layer pumps can be operated at high speeds substantiallywithout impingement damage.

Other problems related to more traditional pumps include vapor lockproblems, and pump efficiencies being limited by affinity laws. The flowto head ratio is often restricted by design limitations in traditionalpumps. Turbulent flow in the stage to stage transition can beproblematic. The down thrust loading developed in some applications canbe excessive. Radial and side loading thrust is often inconsistentrelative to rotational speed. Upon startup, up thrust can be detrimentalto the ultimate balance of the pump. Stated more generally, traditionalpumps are highly subject to vibrations as a natural result of impact ofthe vanes and blades with the fluids pumped. This vibration problem isexacerbated when multiphase fluids are pumped that may include solids,liquids, and gases. Accordingly, the shaft rotation speed of traditionalpumps, especially those used for pumping multiphase fluids, is limitedto avoid destroying the pump due to vibrational damage. The limitedshaft rotational speeds result in lower pump output, limited horsepower,and generally less pumping capability. On the other hand, boundary layerpumps, also referred to herein as “turbomachines”, such as the Teslapump, use flat smooth disks which may be easily balanced and producelittle or no vibration when spinning within a fluid even at relativelymuch higher rotational speeds. Typical boundary layer pumps do notutilize lifting surfaces on the rotating elements. Higher rotationalspeed is directly related to pump flow rates so that boundary layerpumps permit significantly increased pump rotation speeds when pumpingmultiphase fluids which may contain solids, liquids, and gases.Moreover, boundary layer pumps have been found to not only increase theoutput under these difficult pumping conditions as compared totraditional pumps, but also have been found to be much more reliable.

Despite the many advantages of boundary layer pumps over moretraditional pumps for pumping multiphase fluids, and despite commercialusage and considerable interest in boundary layer pumps since theirinvention by Tesla in 1913, solutions to certain multiphase fluidpumping problems utilizing boundary layer pumps have never been found.One example of such pumping problems is found in the oilfield, where itis desirable that multiphase hydrocarbon fluids be pumped in acontinuously upward direction from the production zone of a well througha relatively small wellbore to the surface. In pumps for wellbores, itis therefore desirable that the pump have a small diameter to fit withinthe wellbore. Moreover, pumps with an axial discharge are more efficientfor moving the fluid up the borehole within the confined space of thewellbore and/or production tubing.

The inventors teach herein a novel turbomachine pump, motor andcompressor design which may be utilized as a downhole pump, motor andcompressor that provides the advantages of a boundary layer pump, motorand compressor better suited to handling multiphase fluids with solids,liquids, and gases which are typical of oil and gas wells as comparedwith downhole pumps based on traditional pump designs. The novel pumpmay comprise an axial discharge that may efficiently utilize a straighttubular pump housing whereby fluid is moved through the tubular housing.Moreover, the inventors have determined that it may be desirable thatthe novel pump design of the present invention permit axialinterconnection of any number of identical or substantially identicalaxial flow pump stages to thereby increase the pumping head as desiredwhile keeping the flow rate constant, as is also highly advantageous forwellbore pumping applications where the fluid must be pumped to thesurface from significant depths.

Referring now to the figures, and more particularly to FIG. 1, which istaken from U.S. Pat. No. 7,192,244, there is shown an illustrativeembodiment of multistage boundary layer pump 10. Pump 10 as showncomprises first boundary layer pump stage 12 and second boundary layerpump stage 14 axially interconnected together. The details and operationof multistage boundary layer pump 10 which permit the unique end-to-endinterconnection of multiple boundary layer pump stages is discussedhereinafter. While only two boundary layer pump stages are shown in FIG.1, it will be understood that many more boundary layer pump stages maybe interconnected end-to-end in a similar manner as that shown inFIG. 1. Moreover, each subsequently connected boundary layer pump stagemay be identical or substantially identical to the second boundary layerpump stage 14, if desired. First boundary layer pump stage 12 mayutilize a different inlet 16 to mate with surrounding equipment asdesired. Accordingly, for use in submersible wellbores to pump fluidsfrom a significant depth to the surface, the number of boundary layerpumps utilized may be selected to provide the desired pumping head whilestill maintaining the flow rate of each pump.

As a general overview of operation of an illustrative embodiment of theturbomachine, a fluid enters multistage boundary layer pump 10 at fluidinlet 16, travels through tubular housing 20, and exits at fluid outlet18. Tubular housing 20, in this embodiment, comprises a first tubularhousing section 22 for boundary layer pump stage 12 integral to a secondtubular housing section 24 for boundary layer pump stage 14. If desired,each stage might comprise individual housing sections which areinter-connectable together rather than a single tubular housing for themultiple boundary layer pump stages. Fluid flow arrows indicategenerally the direction of fluid flow through multistage boundary layerpump 10.

An outer support frame comprising bolts 26 and 28 which secure endpieces 30 and 32 together on opposite ends of tubular housing 20 isshown and may be used for conveniently testing, changing out components,and changing the number of boundary layer stages of multistage boundarylayer pump 10 as desired. However, the outer support frame may bemodified, eliminated, or altered as desired depending on the preferredusage of multistage boundary layer pump 10.

An enlarged view of one possible embodiment of a first boundary layerpump stage 40 is shown in FIG. 2 which is taken from U.S. Pat. No.7,192,244. Operation of all boundary layer stages utilized in a multiplestage boundary layer pump may preferably be substantially the samealthough as noted above the suction pump inlet 42 for the first boundarylayer pump stage may be varied in some applications as may be desiredsuch as for interconnecting with existing or standard equipment.

In this illustrative embodiment, drive shaft 44 extends through firstboundary layer pump stage 40 and may be driven by a motor (shown inFIGS. 3, 5 & 6 below) such as a downhole submersible pump drive motor.The motor is a variable speed motor in another embodiment, discussedbelow in relation to FIGS. 3, 5 & 6. Drive shaft 44 may then be utilizedto rotate end cone 46. In this embodiment, keys 48 secure drive shaft 44to end cone 46 for rotation therewith but other suitable means may alsobe utilized for this purpose. Through bolts or studs, such as bolts orstuds 50 and 52, extend from end cone 46 to end ring 54 where they maybe secured utilizing threaded nuts such as threaded nut 56. A pluralityof circumferentially spaced bolts including bolts 50 and 52 may beutilized for this purpose. The bolts are utilized to secure rotorelements 58 in position to form the pump rotor 100. The radialpositions, diameter, cross-sectional shape, number, and other featuresthe bolts may be altered as desired. Various different means are knownfor securing rotor elements together and/or to rotor 100 and/or to adrive shaft. Accordingly, other means may be utilized for securing rotorelements to form pump rotor 100. In this embodiment, fifteensubstantially identical rotor elements 58 are secured between end cone46 and end ring 54. In the present illustrative embodiment, the rotorelements are conical shaped. The rotor elements 58 may be spaced axiallyapart from each other utilizing spacers 60 positioned between each rotorelement. It should be mentioned here that while it is anticipated thatrotor elements are secured together, that the general means for doingso, the shapes of the rotors including internal and external profiles,the shape of internal wall 62 (shown in this example to be substantiallycylindrical except for rifling or spiral grooves) may vary. Each rotorelement 58 may vary in size or shape. In this embodiment, each of spacedapart radial fluid flow paths 64 are defined by rotor elements 58 aresubstantially parallel with respect to each other but this may not bethe case if different size, width, shaped, internal diameter, orexternal diameter rotor elements are utilized.

However, in accord with a presently illustrative embodiment of thepresent invention at least some, and more likely all rotor elements 58may preferably comprise at least a portion thereof which is conical ordome-shaped for purposes of producing within a limited space or diameteran axial flow component for fluid which is also directed radiallyoutwardly in the plurality of radial fluid paths 64 defined between theaxially spaced apart rotor elements 58 to thereby provide an axialdischarge boundary layer pump. As used herein, conical refers to athree-dimension cone, or portion thereof, with sides which may bedefined by straight lines. Dome-shaped is used to describe any curved,convex, concave, s-curved, exponential curve, variable curve or othershape elements or portions thereof which are radially symmetrical asviewed from the end.

If unlimited space were available, and if axial pump multi-staging wereunnecessary, then the direction of fluid flow from a prior art boundarylayer pump could simply be changed by gradual bends in the outputpipeline in which the fluid flows without significantly affecting theenergy that had been imparted to the fluid. However, by utilizing theaxial flow component imparted to the fluid, the pressurized fluid may bedirected within the confines of the pump chamber itself to an axiallypositioned outlet, such as fluid outlet 66, and thereby provide an axialdischarge for boundary layer pump 40 in accord with the presentinvention. The subsequent discussion lists several components ofboundary layer pump 40 which may be utilized in concert but which mayalso be used independently for smoothly directing the fluid flowaxially. As Tesla noted, to effect efficiency in a boundary layer pump,sudden changes in velocity while the fluid is receiving energy fromrotor 100 should be avoided. Accordingly, in one embodiment of thepresent invention, boundary layer pump 40 comprises components asdiscussed in more detail hereinafter which are designed to cooperate toimpart kinetic energy to fluid from rotor 100 and to increase the axialvelocity component of the fluid flow by directing of fluid movement inas smooth manner a manner as possible and without decreasing the overallmagnitude of the kinetic energy (one-half mass times velocity squared)and/or the total kinetic and potential energy imparted to rotor 100.Energy is imparted from rotor 100 to the fluid as the fluid is carriedby rotor 100 in accord with boundary layer pump operation and as thefluid is accelerated radially outwardly by rotor 100. Other discussionsof boundary layer pumps, some of which are provided herein, areavailable to show that the radial distance or radius of rotor 100 andthe rotational speed of rotor 100 largely determine the amount of energyimparted from rotor 100 to the fluid. Bournelli's equation which relatespressure, speed, and height at two points in a steady-flowing,non-viscous, incompressible fluid provides some insights intotransforming the energy imparted to the fluid by rotor 100 such that theaxial component of velocity may be increased in the present invention asdesired to provide an axial discharge boundary layer pump within aconfined space.P.sub.1+½.rho.v.sub.1.sup.2+.rho.gy.sub.1=P.sub.2+½.rho.v.sub.2.sup.2−+.rho.gy.sub.2

-   where P=pressure,-   v=velocity-   .rho.=density-   g=gravitational force-   y=height-   and ½.rho.v.sup.2=kinetic energy;    where in boundary layer pump 40 the velocity vector has an axial    component and a radial component and an overall magnitude.

In the illustrative embodiment shown in FIG. 1 and FIG. 2, rotorelements 58 are conical rings which are angled at forty-five degreeswith respect to the axis of rotation of rotation. In this embodiment,the boundary layer effect induces fluid flow through radial passageways64 at an angle of forty-five degrees. In one embodiment of theinvention, a plurality of spiraling fluid paths 68 are provided whichencircles rotor 100 and receive the fluid flow to which energy has beenimparted so as to smoothly guide the fluid flow toward fluid outlet 66.While one presently illustrative embodiment is shown, it will beunderstood that the invention is not limited to this particularconfiguration. Numerous different possibilities exist for variations inwall 70, radial flow paths 60, and fluid paths 68 to provide a fluidwith kinetic energy wherein the axial velocity vector component maycontinuously increase without decreasing significantly the magnitude ofthe kinetic energy while experiencing the benefits of a boundary layerpump.

As one possible construction variation, the angle of the spiral fluidpaths may change. For instance, it may be desirable that the angle ofthe spiral of fluid path 68 smoothly increase as the fluid flow pathnears fluid output 66 so that the axial velocity component of thekinetic energy increases significantly by gently redirecting thedirection of flow path 68. This could be matched, if desired, by adecreasing angle of radial flow paths 60 formed between rotor elements58, e.g. down to thirty degrees' or any other selected angle.Alternatively, radial flow paths 60 may be oriented to be greater thanforty-five degrees, e.g. sixty degrees whereby the magnitude of thevelocity vector in the radial direction may be initially increased ascompared to the velocity vector in the axial direction. The angle ofspiral fluid path 68 may then be utilized to smoothly redirect thedirection of the fluid flow axially without significantly reducing soproduced fluid kinetic energy. Moreover, instead of one or more spiralfluid paths 68 formed within wall 70, a volute region around rotor 100may be utilized with wall 70 being substantially smooth. Or acombination of a volute section and fluid spiral paths 68 may beutilized. Moreover, while wall 70 is shown as cylindrical in thisembodiment, wall 70 could have other preferably smooth shapes such asrounded, venturi-shaped, concave, or the like, as desired, to therebygradually direct fluid in the desired direction such as to provide anaxial discharge from boundary layer 40. Moreover, wall 70 may also beconical so that in combination with an increasing angle of fluid path 68and radial flow paths 60 the energy in the fluid is increasinglydirected axially to smoothly direct the overall fluid radially inwardlybefore leaving outlet 66. It will be noted that in one presentlyillustrative embodiment as shown in FIG. 1 and FIG. 2 transition section72 may include conical wall 74. In yet another embodiment, spiralgrooves 68 may not be utilized at all whereby the shape of internal wall62, which may be cylindrical, conical, venturi-shaped or the like may beutilized to largely redirect the energy of the fluid flow in the axialdirection. Accordingly, while one possible embodiment of the presentinvention is as shown, it will be appreciated that numerousconstructions and methods may be utilized for providing a compact radialdischarge axial pump 40 in accord with the present invention.

Other information concerning boundary layer pumps is relevant fordetermining the sizes and positioning of various pump components.Pumping effects of features such as inner hole diameter 76 of rotorelements 58, the number of rotor elements 58, rotor element thickness,various means for mounting rotor elements 58 to a shaft (if desiredalthough in the present embodiment the rotor elements are not mounteddirectly to a shaft), outer volute and housing or volume which surroundsrotor 100 (which for instance would apply to the size of channels 68 inthe pictured embodiment but would also apply if channels 68 are notutilized and a volume is provided around rotor 100), inlet 42 and outlet66 sizes, rotational speeds, the relationship of pressure/volume andhorse power, and the general pump formula. The values of thesecomponents require knowledge of the particular pumping application.Other helpful boundary layer pump design information may include theunclassified article “Performance of Multiple-Disk-Rotor Pumps withVaried Interdisk Spacings,” by Joseph H. Morris, David W. Taylor, NavalShip R&D Center August 1980, Report No DTNSRDC-80/008, Govt Accession NoAD-A088010, Naval Sea Systems Command (SEA 05R14), Washington, D.C.20362, which describes disk-rotor pumps having various configurationswith interdisk spacing ranging from 0.006 to 0.26 inches which wereinvestigated at operating speeds from 3550 to 7000 revolutions perminute whereby operating data for the pumps with the various rotors isprovided. It is noted that the report concludes that good performance atwide interdisk spacings was obtained. A review of that data indicatesthat a fairly wide range of interdisk spacings may be utilized with goodpump performance wherein the range utilized may be selected for thefluids to be pumped. Because boundary layer pump 40 operates on similarboundary layer principals, the above information is useful fordetermining the various factors for a desired pump output of boundarylayer pump 40 in accord with the present invention.

As discussed hereinbefore, in one embodiment of the present invention itis desirable to provide a multi-stage boundary layer pump, one possibleembodiment of which is shown in FIG. 1. Accordingly, characteristics ofa transition zone, such as transition zone 72 of FIG. 2 or transitionzones 78 and 80 in FIG. 1, are utilized to smoothly transition theenergy in fluid from one pumping stage to the next pumping stage withoutsubstantial energy loss.

In FIG. 1, it is seen that transition zones 78 and 80 comprise conicalwalls 82 and 84 which smoothly direct fluid flow from the volute orregion or channels 22 which surround the rotor. Conical walls provide asimple and smooth transition but other shapes may also be utilized suchas concave, convex, s-shaped, french curved walls, and the like, asdesired. The diameter of inlet region 86 may be selected as desiredbased on the relative diameter or combined diameters of channels 22 orthe volute region surrounding the rotors to thereby provide as smoothand gradual changes to the fluid velocity and direction as possible. Inone embodiment of the invention for use in a wellbore, the outerdiameter of housing 20 is approximately four and five eighths inches andrelative size of the components shown in FIG. 1 is substantiallyproportional to that shown. Fifteen rotor elements are utilized perstage with one-eighth inch spacing. In testing of this design, it wasfound that the best efficiency for 4500 TDH (total dynamic head) was at1750 BPD (barrels per day). Utilizing water with air infusion it wasfound stage efficiency was 13% with 1.8 HP (horsepower) at 60 Hz.Existing technology for downhole applications utilize 60 Hz to avoidexcessive vibration but multistage boundary layer pump 10 was operatedat 90 Hz without noise or vibration. Thus, the flow rates, horsepower,and pumping capabilities can be increased by use of higher RPM. In othertesting, with 50% entrained gas in a fluid pumped by pump 10,substantially no cavitation was produced. In prior art, downhole pumps,this amount of gas in fluid can cause significant problems.

Other elements utilized in transition zones 78 and 80 for the presentembodiment of boundary layer multistage pump 10 comprise bearingassemblies 88 and 90 for the corresponding rotors. Bearing assembly 110comprises a radial bearing with stator 114 and diffuser 112. Radialbearing assembly 110 radially supports drive shaft 44 (shown in FIG. 2)or drive shaft 92 (shown in FIG. 1) with respect to the pump. Diffuser112 mates with the drive shaft and rotates within stator 114 alongmating conical surfaces within stator 114 and diffuser 112. Due to theconical surfaces which are also utilized for directing fluid flow,thrust support in one direction along drive shaft 92 is also provided byradial bearing assembly 112. Stator 114 fits between the pumping stagesand may utilize ring 118 or other means to axially and radially affixstator 114 with respect to tubular housing 20. Diffuser 112 also acts tomaintain laminar flow and smoothly directs the flow from one pumpingstage to the next. The fluid flow through radial bearing 110 cools andlubricates the bearing. Within transition sections 78 and 80, the fluidflow is directed to conical surfaces 82 and 84 (see FIG. 1) withinstator 114 and preferably through fins of diffuser 112. Fins maypreferably be oriented in line with the direction of laminar flow toguide the flow to the next stage. Diffuser 112 may be designed to rotateto good effect as desired. The subsequent stages then start with thereleased fluid flow and pressure of the previous stage, whereby eachstage compounds the pressure to the next stage. The number of stagesdepends on the total lift required and the head for the application andthe volume of the fluid. These are a function of the diameter rotorelement 58 rim speed, viscosity, solids (size), the number of rotorelements 58, and the spacing of rotor elements 58. It will be seen thata continuous geometry is utilized through the transition region from theend of the last rotor element 58 to the intake of the first rotorelement 58 in the next stages. In one illustrative embodiment, thetransition zone provides a continuous spiraling flow that ensures thefluid motion is smoothly directed to the next pumping stage. Whileradial bearing assembly 110 is a presently illustrative embodiment fordownhole pumping, other bearing assemblies may also be utilized.

In summary, referring to multistage boundary layer pump 10 in FIG. 1generally and FIG. 2 for enlarged component details, fluid flow entersinput 16 (FIG. 1) and flows to the rotor elements 58 (FIG. 2) whererotational energy of rotor 100 (FIG. 1) is imparted to the fluid as thefluid is accelerated radially outwardly by rotor 100 through radial flowpassages 64 between spaced apart rotor elements 58. The fluid exitsrotor 100 in this embodiment into a plurality of spiraling flow paths 68which surround rotor 100. The fluid has an axial velocity component dueto the angle of flow paths 68. The spiraling flow paths may be utilizedto maintain laminar fluid flow at about the same axial velocity, if thatis the desired design goal. At the end of the spiraling flow paths 68,the fluid is directed along conical surfaces, such as conical surface 82of stator 80 as shown in FIG. 1 or within stator 114 shown in FIG. 6wherein stator 114 comprises part of the radial bearing assemblyutilized to support the drive shaft. The fluid is therefore smoothlydirected to the next pumping stage 14 whereupon the same process occursand the pump pressure increases.

Turning now to FIG. 2, in FIG. 2, it is seen that transition zones 78and 80 comprise conical walls 82 and 84 which smoothly direct fluid flowfrom the volute or region or channels 22 which surround the rotor.Conical walls provide a simple and smooth transition but other shapesmay also be utilized such as concave, convex, s-shaped, French curvedwalls, and the like, as desired. The diameter of inlet region 86 may beselected as desired based on the relative diameter or combined diametersof channels 22 or the volute region surrounding the rotors to therebyprovide as smooth and gradual changes to the fluid velocity anddirection as possible. In one embodiment of the invention for use in awellbore, the outer diameter of housing 20 is approximately four andfive eighths inches and relative size of the components shown in FIG. 1is substantially proportional to that shown. Fifteen rotor elements areutilized per stage with one-eighth inch spacing. In testing of thisdesign, it was found that substantial efficiency for 4500 TDH (totaldynamic head) was at 1750 BPD (barrels per day). Utilizing water withair infusion it was found stage efficiency was 13% with 1.8 HP(horsepower) at 60 Hz. Existing technology for downhole applicationsutilize 60 Hz to avoid excessive vibration but multistage boundary layerpump 10 has been operated at 90 Hz without noise or vibration. Thus, theflow rates, horsepower, and pumping capabilities can be increased by useof higher RPM. In other testing, with 50% entrained gas in the fluidpumped by pump 10, substantially no cavitation was produced. The flowrates, horsepower, and pumping capabilities can be decreased by use oflower RPM. In prior art, downhole pumps, this amount of gas in fluid maycause significant problems. The outer diameter of the housing can beenlarged to handle larger solids in the fluid. The outer diameter of thehousing can be reduced to handle smaller diameter operations.

Turning now to FIG. 3, as shown in FIG. 3 an illustrative embodiment isshown for pumping a multiphase fluid 131 using a modified version 300 ofthe turbomachine pump stage 40 which in the present illustrativeembodiment is a bladeless turbine pump. As shown in FIG. 3, theturbomachine pump 101 is deployed down a wellbore 118 inside of drillpipe 166 or pipeline attached to a drilling rig 120. A motor 110 isconnected to pump 101 to provide rotation to the pump 100. Aturbomachine controller 112 (also referred to herein as a turbomachineprocessor) is in data communication with the motor. Data communicationis used herein to mean that analog and digital data is exchanged betweenthe motor 110 and the turbomachine processor 112. The turbomachineprocessor is in data communication with the motor. In another embodimentsensors on the motor and with sensors and a processor on theturbomachine pump, indicating motor operating characteristics includingbut not limited to revolutions per minute and current being drawn. Theturbomachine processor communicates with the motor processor and stageprocessor on the turbomachine pump 101. A computer program is stored incomputer readable medium 114. The turbomachine processor executes thecomputer program. The computer program includes but is not limited tocomputer instructions that are executed by the processor. Theturbomachine pump 101 includes but is not limited to a turbomachine pump101, a fluid port 134 and a solids port 133. Multiphase fluid 131 ispumped from the wellbore 118 through the turbomachine pump 100 locatedin drill pipe 116. The multiphase fluid includes solids, liquid fluidsand fluid gas. The solids are ported from the fluid 131 in pump 101through solids port 132. Fluids and gas are ported from the fluid 131 inpump 100 through fluid port 134. In a particular embodiment, theturbomachine pump, fluid port and solids port act to clean up themultiphase fluid 131 to provide the filtered gas/fluid 130 (“cleaned-up”fluid) to pump 138 which can be a pump that is not capable ofefficiently handling the solids in the multiphase fluid. Each of theembodiments disclosed herein can be deployed in a drill pipe 116 and apipeline 117.

Turning now to FIG. 4, an illustrative embodiment 400 of a multi-stageturbomachine pump is illustrated showing pump stages 1-N deployed in adrill pipe 116. Each stage of the multi-stage turbomachine pump feeds asubsequent stage to increase pumping capacity. Each stage of theturbomachine pump is filtered so that the fluid is lighter and containsless solids as it passes through each successive stage of themulti-stage turbomachine pump.

Turning now to FIG. 5, an illustrative embodiment 500 of a turbomachinecompressor 100 is illustrated. As shown in FIG. 5 the compressor usingthe turbomachine pump 100 compresses lower pressure gas 510 to form highpressure gas 512. The high-pressure gas 512 is compressed and pumpedthrough the drill pipe 116 to the storage tank 122 and stored underpressure on the surface. The compressor is also deployed in a midstreampipeline for transportation of the high-pressure gas under pressure fromthe storage tank to a downstream processing plant.

Turning now to FIG. 6, FIG. 6 illustrates a side view of an illustrativeembodiment, a turbomachine motor 103 is provided. A hydraulic pump 602provides fluid 604 to the turbomachine motor 103. The fluid 604 flowsthrough the turbomachine motor and causes rotor elements in theturbomachine motor 100 to rotate. As the turbomachine motor rotates, theturbomachine motor drives equipment 150. In one illustrative embodiment,the equipment 150 is a drill bit.

Turning now to FIG. 7, a multi-stage turbomachine motor is depictedshowing turbomachine motor stages 1-N deployed in a pipeline 117. Inanother embodiment turbomachine motor stages 1-N deployed in a drillpipe 116. Each stage of the multi-stage turbomachine motor feeds asubsequent stage to increase motor capacity.

Turning now to FIG. 8, a multi-stage turbomachine pump is depictedshowing turbomachine motor stages 1-N deployed in a pipeline 117. Inanother embodiment turbomachine motor stages 1-N are deployed in a drillpipe 116. Each stage of the multi-stage turbomachine pump feeds asubsequent pump stage to increase pumping and filtering solids capacity.Each stage of the turbomachine pump is filtered so that the fluid islighter and contains less solids as it passes through each successivestage of the multi-stage turbomachine pump. In an embodiment, the motor110 is a variable speed motor. In this embodiment, the turbomachineprocessor sets the speed and path width between rotor elements based onthe lighter fluid density, FD. Thus, the lighter the fluid the fasterthe rpm of the rotor elements driven by variable speed motor 110 asdiscussed next regarding FIG. 9A and FIG. 9B.

Turning now to FIG. 9A and FIG. 9B, as shown in the schematic depictionof FIG. 9A and FIG. 9B, a distance 710 between the rotor elements 58(which can be disk and also be conical element is dynamically adjustableto accommodate efficiently moving or pumping varying density fluidsmoving through the bladeless rotary machine when used as a pump. Thespacing “d” 710 between the rotor elements 58 (disks d 710 or conicalelements) is adjusted to accommodate efficiently generating rotationalkinetic energy as a motor generated from moving varying density fluidsmoving through the bladeless rotary machine when used as a motor. Whenused as a pump, the conical elements and disk rotor elements 58 rotateto impart acceleration of a working fluid through the spaces between thedisks or conical elements using boundary layer adhesion techniques. Theworking fluid, which can be a liquid, a gas or a liquid containingsolids, is smoothly directed to any number of subsequent boundary layerpumping or motor stages which are axially positioned with respect toeach other. The working fluid is typically a multiphase fluid containingliquid, gas and solids. For lower density (D) fluids such as gas, theaxial distance d 710 between the conical and disk elements is adjustedto be smaller than a distance d between the conical and disk elementswhen a heavier fluid is passing through the rotary machine. An axialcoupling 705 is provided between the disks to enable adjusting the axialdistance between the disks. In an embodiment, the axial coupling is anexpandable bellows axial coupling is pressurized to increase the axialdistance d 710 between the disk elements 704. In a particularembodiment, the axial coupling is a mechanical axial coupling isactuated to increase the axial distance d 710 between the disk elements704. In a particular embodiment, the axial coupling is an elastomericaxial coupling is actuated to increase the axial distance d 710 betweenthe disk elements 704.

As shown in FIG. 10, a cross sectional view of an illustrativeembodiment of the invention is shown having an auger coupling housing929 containing an auger coupling to enhance fluid flow between upperpump 940 and lower pump 950 in a pipeline 117. auger coupling housing929 containing an auger coupling to enhance fluid flow between upperpump 940 and lower pump 950 in a drill pipe 116. In another embodiment,the auger coupling is deployed. In the past, pumps such as pumps 940 and950 and pump sections 1102 have been connected to each other in a linewith solid shaft couplings that do little or nothing to enhance andcomplement fluid flow between pumps or pump sections. In an illustrativeembodiment of the invention, an auger coupling is provided to enhanceand complement fluid flow in the coupling section of the pipe line ordrill pipe between upper pump 940 and lower pump 950 and pump sections1102 and help flow by contributing to laminar flow of fluid and gasbetween pumps 940 and 950 and pump sections 1102 in the coupling sectionoccupied by auger coupling. An auger 930 is formed on the outside acentral spline 927. An upper pump 940 and a lower pump 950 shafts 910and 920 are connected using auger coupling inside of auger couplinghousing 929. The central spline receives the lower portion 910 of pumpshaft for the upper pump and upper portion 920 of the pump shaft for thelower pump 950. The auger coupling is placed in an adaptor housing 929that is used to mechanically connect the upper pump and lower pumps tothe auger coupling. Flanges 922 formed on the adaptor housing 929 thatconnect the upper and lower pump and engage the lower pump upper shaftand the lower pump upper shaft. The auger coupling connects the upperand lower sections of a fluid pipe or pipe line containing fluid pumpedby the upper and lower pumps. In one particular embodiment, the splineis a hollow tube that allows fluid flow through it. The auger couplinghelps insure efficient transfer of fluid flow between pumps or pumpsections. The auger coupling compliments fluid flow between pumps orpump sections connected using the auger coupling. In a particularembodiment, the upper and lower pumps can be any type of pump includingbut not limited to a turbomachine, an auger pump and a centrifugal pump.In a particular embodiment, the auger coupling induces flow between theupper and lower pump. The auger coupling creates additional pumpingpressure in the fluid in coupling section between fluid sections. Theauger coupling performs lifting work on the fluid in the drill pipe orpipe line as the fluid exits one pump section and enters another pumpsection.

As shown in FIG. 11, in a particular embodiment, twenty-one-footsections of modular pumps are joined together to form 20-foot sectionsof pumps 1102 in a pipe line 117. In another particular embodiment,twenty-one-foot sections of modular pumps are joined together to form20-foot sections of pumps 1102 in a drill pipe 116. The 20-foot sectionsof pumps 1102 are joined by the auger coupling in auger coupling housing929. The auger coupling 1000 induces fluid flow in the pipeline 1104. Ina particular embodiment, the auger coupling 1000 continues boundarylayer flow between 20-foot sections of pumps 1102 in a drill pipe and ina pipeline.

Turning now to FIG. 12A, in a particular illustrative embodiment, theturbomachines are used as a turbine motor and as a pump in pipeline 117.In a particular illustrative embodiment, the turbomachines are used as aturbine motor and as a pump in drill pipe 116. The shaft 1201 spins theturbomachine motor 1212 so that the turbomachine motor 1212 generateshorse power to help turn the shaft 1201. In a particular embodiment, theturbomachine motor generated horsepower is applied to the shaft that isbeing driven by the motor 1208 that applies the horsepower to turn theshaft 1201. The horse power generated by the turbine reduces the motorhorse power requirements to turn the shaft. As shown in FIG. 12 pump1202 (which is a turbomachine pump or other type of pump) pumps fluidprovided through intake 1204. A seal-chamber section (also referred toherein as a shaft seal section) 1206 is provided below the pump 1202 andabove motor 1208. American Petroleum Institute Recommended Practice (APIRP) 11S7 gives a detailed description of the design and functioning oftypical seal-chamber sections. An upside-down shaft seal section 1210 isprovided below the motor 1208. A turbomachine motor 1212 is providedabove pump intake 1214. The turbomachine pump 1212 is rotated by theshaft 1201 and which generates horsepower that is applied to rotate theshaft 1201 reduces the horsepower requirements on motor 1208. A fluid inthe wellbore in which the turbomachine pump and motor are placed ispassed through the turbomachine motor to the pumps 1202. In FIG. 12Bpumps, which can be a combination of any type pump such as areciprocation pump and a turbomachine pumps 1202 are connected to theturbomachine motor 1212 in a pipeline 117. A seal section is below thepump and above the motor. A sensor 1220 is located below the motor. Inanother the combination of any type pump such as a reciprocation pumpand a turbomachine pumps 1202 are connected to the turbomachine motor1212 in a drill pipe 116.

As shown in FIG. 13, in an illustrative embodiment is depicted 1300. Apump 1302 is connected to another pump 1306 using an auger coupling inauger coupling housing 929 deployed in a pipeline 117 as shown in FIG.10. In another embodiment pump 1302 is connected to another pump 1306using an auger coupling in auger coupling housing 929 deployed in adrill pipe 116. A second auger coupling 1308 having intake 1309. A sealsection 1310 is provided above motor 1312.

Turning now to FIG. 14, a cross section drawing 1400 of an illustrativeembodiment of a progressive staged filter deployed in a pipe line 117 isdepicted. In another illustrative embodiment of the progressive stagedfilter deployed in a drill pipe 116 is depicted. The axial distance d710 between the conical and disk elements is adjusted to be smaller thana distance d between the conical and disk elements when a heavier fluidis passing through the rotary machine. Dense fluids 1402 having firstdensity D1 enter a first turbomachine pump stage 1403 where the densefluid is pumped and filter. Turbomachine filter stage 1 has a distanced1 between conical elements. The denser portions of the fluid 1402 aredischarged by pump stage 1 as discharge fluid 1405. The filtered fluid1401 from pump stage 1 is fed to pump stage 2 1406. The axial distance d710 between the conical and disk elements is adjusted to be smaller thana distance d between the conical and disk elements when a heavier fluidis passing through the rotary machine. The axial distance d1 for pumpstage 1 is set to pump the dense fluid 1402 having a density D1.Turbomachine filter stage 2 has a distance d2 between conical elements.The denser portions of the fluid 1401 are discharged by pump stage 2 asdischarge fluid 1407. The filtered fluid 1408 from pump stage 2 is fedto pump stage 2 1409. Turbomachine filter stage 3 has a distance d3between conical elements. The denser portions of the fluid 1407 aredischarged by pump stage 3 as discharge fluid 1409. The filtered fluid1414 from pump stage 3 is fed upward. Fluid density D3 is less thanfluid density D2. Fluid density D2 is less than fluid density D1. Thedistance d1 between conical elements in pump stage 1 for larger than thedistance d2 between conical elements in pump stage 2. The distance d2between conical elements in pump stage 2 for larger than the distance d3between conical elements in pump stage 3. In the progressive filter, thefluid density of pumping stage 1 is D1 and is denser than fluid densityD2 of the fluid being pumped by pumping stage 2. The fluid density ofpumping stage 2 is D2 and is denser than fluid density D3 being pumpedby pumping stage 3.

The present invention can be realized in hardware, software, or acombination of hardware and software. In a specific embodiment, a systemaccording to the present inventions can be realized in a centralizedfashion in one computer system, or in a distributed fashion wheredifferent elements are spread across several interconnected computersystems. Any kind of computer system or other apparatus adapted forcarrying out the methods and inventions described herein may be used forpurposes of the present inventions. A typical combination of hardwareand software could be a general-purpose computer system with a computerprogram that, when being loaded and executed, controls the computersystem such that it carries out the methods and inventions describedherein.

The figures herein include block diagram and flowchart illustrations ofmethods, apparatus(s) and computer program products according to variousembodiments of the present inventions. It will be understood that eachblock in such figures, and combinations of these blocks, can beimplemented by computer program instructions. These computer programinstructions may be loaded onto a computer or other programmable dataprocessing apparatus to produce a machine, such that the instructionswhich execute on the computer or other programmable data processingapparatus may be used to implement the functions specified in the block,blocks or flow charts. These computer program instructions may also bestored in a computer-readable medium or memory that can direct acomputer or other programmable data processing apparatus to function ina particular manner, such that the instructions stored in thecomputer-readable medium or memory produce an article of manufactureincluding instructions which may implement the function specified in theblock, blocks or flow charts. The computer program instructions may alsobe loaded onto a computer or other programmable data processingapparatus to cause a series of operational steps to be performed on thecomputer or other programmable apparatus to produce a computerimplemented process such that the instructions which execute on thecomputer or other programmable apparatus provide steps for implementingthe functions specified in the block, blocks or flow charts.

Those skilled in the art should readily appreciate that programsdefining the functions of the present inventions can be delivered to acomputer in many forms, including but not limited to: (a) informationpermanently stored on non-writable storage media (e.g., read only memorydevices within a computer such as ROM or CD-ROM disks readable by acomputer 110 attachment); (b) information alterably stored on writablestorage media (e.g., floppy disks and hard drives); or (c) informationconveyed to a computer through communication media for example usingwireless, baseband signaling or broadband signaling techniques,including carrier wave signaling techniques, such as over computer ortelephone networks via a modern, or via any of networks.

The term “executable” as used herein means that a program file is of thetype that may be run by the Turbomachine processor 110. In specificembodiments, examples of executable programs may include withoutlimitation: a compiled program that can be translated into machine codein a format that can be loaded into a random access portion of theComputer Readable. Medium 128 and run by the Turbomachine processor 110;source code that may be expressed in proper format such as object codethat is capable of being loaded into a random access portion of theComputer Readable Medium 128 and executed by the Turbomachine processor110; or source code that may be interpreted by another executableprogram to generate instructions in a random access portion of theComputer Readable Medium to be executed by the Turbomachine processor110. An executable program may be stored in any portion or component ofthe Computer Readable Medium including, for example, random accessmemory (RAM) read-only memory (ROM), hard drive, solid-state drive, USBflash drive, memory card, optical disc such as compact disc (CI)) ordigital versatile disc (DVD), floppy disk, magnetic tape, or othermemory components.

The Computer Readable Medium may include both volatile and nonvolatilememory and data storage components. Volatile components are those thatdo not retain data values upon loss of power. Nonvolatile components arethose that retain data upon a loss of power. Thus, the Computer ReadableMedium may comprise, for example, random access memory (RAM), read-onlymemory (ROM), hard disk drives, solid-state drives, USB flash drives,memory cards accessed via a memory card reader, floppy disks accessedvia an associated floppy disk drive, optical discs accessed via anoptical disc drive, magnetic tapes accessed via an appropriate tapedrive, and/or other memory components, or a combination of any two ormore of these memory components. In addition, the RAM may comprise, forexample, static random access memory (SRAM), dynamic random accessmemory (DRAM), or magnetic random access memory (MRAM) and other suchdevices. The ROM may comprise, for example, a programmable read-onlymemory (PROM), an erasable programmable read-only memory (EPROM), anelectrically erasable programmable read-only memory (EEPROM), or otherlike memory device.

In a specific embodiment, the Turbomachine processor may representmultiple Turbomachine processors and/or multiple processor cores and theComputer Readable Medium may represent multiple Computer ReadableMediums that operate in parallel processing circuits, respectively. Insuch a case, the local interface may be an appropriate network thatfacilitates communication between any two of the multiple Processors,between any processor and any of the Computer Readable Medium, orbetween any two of the Computer Readable Mediums, etc. The localinterface may comprise additional systems designed to coordinate thiscommunication, including, for example, performing load balancing. TheTurbomachine processor may be of electrical or of some other availableconstruction.

In a particular illustrative embodiment, A rotary machine operable fortransformation of energy between rotary mechanical energy and fluidkinetic energy is disclose, the rotary including but not limited to adrive shaft; a tubular housing defining a fluid input and a fluid outputand a rotor operating region; a rotor mounted within the rotor operatingregion for rotation about a rotor axis of rotation through the driveshaft, the rotor comprising a first rotor end and a second rotor end,the axis of rotation extending between the first rotor end and thesecond rotor end, the rotor operating region being positioned betweenthe fluid input and the fluid output; and a plurality of rotor elementsfor the rotor, the plurality of rotor elements being axially spaced fromeach other along the rotor, the plurality of rotor elements comprising aplurality of surfaces oriented on the rotor so as to be concentric tothe rotor axis of rotation, the plurality of rotor elements axiallyspaced a distance RD between the rotor elements, defining therebetween aplurality of radial flow paths each having a path width PW defined bythe distance RD between the rotor elements, the plurality of rotorelements defining a plurality of centrally positioned apertures thatcollectively define an unrestricted interior opening that surrounds thedrive shaft and connects to the plurality of radial flow paths to permitradially outwardly fluid flow through the plurality of radial flowpaths, the unrestricted interior opening receiving fluid flow from thefluid input to provide the radially outwardly fluid flow through theplurality of radial flow paths; and a solids port through which thesolids are removed from the fluid. In another particular embodiment ofthe invention, the solids port through which the solids are transferredfrom the tubular housing, the rotary machine further including but notlimited to a fluid port though which the fluid is transferred from thetubular housing, wherein the solids port and the fluid port are twoseparate ports. the rotary machine is a centrifugal fluid separator thatseparates a gas from the fluid, the rotary machine further including butnot limited to a gas port though which the gas is transferred from thetubular housing. In another particular embodiment of the invention, therotary machine further includes but is not limited to a motor attachedto the drive shaft. In another particular embodiment of the invention,the rotary machine includes but is not limited to a plurality of stackedrotary machines used as an inline pump in pipelines to boost fluid flow.In another particular embodiment of the invention, the rotary machinecomprises a plurality of stacked rotary machines used to compress thefluid when the fluid is a gas. In another particular embodiment of theinvention, the rotary machine is used as a jet engine. In anotherparticular embodiment of the invention, the rotary machine is used topropel a ship. In another particular embodiment of the invention, theplurality of stacked rotary machines is used to pump provide more headthan a single rotary machine and have a smaller diameter housing than asingle rotary machine housing diameter.

In another particular embodiment of the invention, the rotary machine isused as an injection pump to provide high pressure pumping from surfaceto deep downhole being able to handle pressure changes, cavitation andsolids. In another particular embodiment of the invention, the rotarymachine is used to dewater mines, wherein the rotary machine carriesheavy abrasives without substantial impingement wear. In anotherparticular embodiment of the invention, the tubular housing has ahousing diameter HD, wherein the housing diameter is selected based onthe density of the fluid FD, wherein the selected housing diameter HD isproportional to the density of the fluid FD. In another particularembodiment of the invention, the rotary machine further including butnot limited to a motor attached to the drive shaft; a processor in datacommunication with a computer readable medium and the motor; and acomputer program stored in the computer readable medium, the computerprogram comprising instructions executed by the processor, the computerprogram further comprising instructions to adjust a speed value for themotor wherein the speed value is adjusted inversely proportional to adensity FD of the fluid. In another particular embodiment of theinvention, the motor is an electric motor and density FD of the fluid isestimated by current flowing to the electric motor. In anotherparticular embodiment of the invention, the drive shaft furthercomprises a variable distance element. In another particular embodimentof the invention, the computer program further including but not limitedto instructions to adjust the variable distance element from a firstdistance value RD1 for the space between the rotor elements to adistance value RD2 for the space between the rotor elements based on adensity FD of the fluid. In another particular embodiment of theinvention, the rotary machine further comprises a multi-staged rotarymachine that has a smaller housing diameter HD than a single stagerotary machine. In another particular embodiment of the invention, theplurality of radial flow paths are oriented parallel or substantiallyparallel with respect to each other and are angled between zero andninety degrees with respect to the rotor axis of rotation. In anotherparticular embodiment of the invention, the fluid input is on anopposite end of the tubular housing from the fluid output. In anotherparticular embodiment of the invention, the tubular housing furtherdefines a peripheral fluid flow path along a periphery of the rotor, theperipheral fluid flow path being in communication with the fluid inputand the fluid output, the tubular housing constraining fluid to movewith an axial direction vector component through the fluid input intothe tubular housing, through the peripheral flow path, out of thetubular housing through the fluid output. In another particularembodiment of the invention, the peripheral flow path is substantiallyconcentric with the rotor. In another particular embodiment of theinvention, at least a portion the plurality of rotor elements aresubstantially identical. In another particular embodiment of theinvention, further includes but is not limited to a plurality of tubularhousing sections each defining a fluid input and a fluid output and arotor operating region, the plurality of tubular housing sections beingaxially oriented with respect to each other such that a respectiveoutput of each tubular section is connected to a respective input ofanother tubular section; and a respective rotor for each of theplurality of tubular housing sections mounted within the rotor operatingregion for rotation about a rotor axis of rotation, and a respectiveplurality of spaced rotor elements for each respective rotor, and eachrespective plurality of spaced rotor elements defining a plurality ofradial flow paths therebetween.

In another particular embodiment of the invention, a turbomachinecompressor is disclosed, the turbomachine compressor including but notlimited to a tubular housing defining a fluid input and a fluid outputand a rotor operating region; a rotor mounted within the rotor operatingregion for rotation about a rotor axis of rotation through the driveshaft, the rotor comprising a first rotor end and a second rotor end,the axis of rotation extending between the first rotor end and thesecond rotor end, the rotor operating region being positioned betweenthe fluid input and the fluid output; and a plurality of rotor elementsfor the rotor, the plurality of rotor elements being axially spaced fromeach other along the rotor, the plurality of rotor elements comprising aplurality of surfaces oriented on the rotor so as to be concentric tothe rotor axis of rotation, the plurality of rotor elements axiallyspaced a distance RD between the rotor elements, defining therebetween aplurality of radial flow paths each having a path width PW defined bythe distance RD between the rotor elements, the plurality of rotorelements defining a plurality of centrally positioned apertures thatcollectively define an unrestricted interior opening that surrounds thedrive shaft and connects to the plurality of radial flow paths to permitradially outwardly fluid flow through the plurality of radial flowpaths, the unrestricted interior opening receiving fluid flow from thefluid input to provide the radially outwardly fluid flow through theplurality of radial flow paths. In another particular embodiment of theinvention, the turbomachine further includes but is not limited to amotor attached to the drive shaft; a processor in data communicationwith a computer readable medium and the motor; and a computer programstored in the computer readable medium, the computer program comprisinginstructions executed by the processor, the computer program furthercomprising instructions to adjust a speed value for the motor whereinthe speed value is adjusted inversely proportional to a density FD ofthe fluid. In another particular embodiment of the invention, the motoris an electric motor and density FD of the fluid is estimated by currentflowing to the electric motor. In another particular embodiment of theinvention, the drive shaft further comprises a variable distanceelement, the computer program further comprising: instructions to adjustthe variable distance element from a first distance value RD1 for thespace between the rotor elements to a distance value RD2 for the spacebetween the rotor elements based on a density FD of the fluid. Inanother particular embodiment of the invention, the computer programfurther comprising instructions to adjust the variable distance elementfrom a first distance value RD1 for the space between the rotor elementsto a distance value RD2 for the space between the rotor elements basedon a density FD of the fluid.

In another particular embodiment of the invention, a turbomachine motorfor transformation of energy from fluid kinetic energy to rotarymechanical energy, the turbomachine motor including but not limited to adrive shaft; a tubular housing defining a fluid input and a fluid outputand a rotor operating region; a rotor mounted within the rotor operatingregion for rotation about a rotor axis of rotation through the driveshaft, the rotor comprising a first rotor end and a second rotor end,the axis of rotation extending between the first rotor end and thesecond rotor end, the rotor operating region being positioned betweenthe fluid input and the fluid output; and a plurality of rotor elementsfor the rotor, the plurality of rotor elements being axially spaced fromeach other along the rotor, the plurality of rotor elements comprising aplurality of surfaces oriented on the rotor so as to be concentric tothe rotor axis of rotation, the plurality of rotor elements axiallyspaced a distance RD between the rotor elements, defining therebetween aplurality of radial flow paths each having a path width PW defined bythe distance RD between the rotor elements, the plurality of rotorelements defining a plurality of centrally positioned apertures thatcollectively define an unrestricted interior opening that surrounds thedrive shaft and connects to the plurality of radial flow paths; and afluid supply, wherein a fluid is pumped from the fluid supply to thefluid input to produce rotational motion of the rotor so that theturbomachine motor acts as a hydraulic motor. In another particularembodiment of the invention, the rotary machine drives a downholeequipment in a slim hole environment. In another particular embodimentof the invention, the rotary machine drives a compressor in a downholeenvironment that includes but is not limited to a motor attached to thedrive shaft; a processor in data communication with a computer readablemedium and the motor; and a computer program stored in the computerreadable medium, the computer program comprising instructions executedby the processor, the computer program further comprising instructionsto adjust a speed value for the motor wherein the speed value isadjusted inversely proportional to a density FD of the fluid. In anotherparticular embodiment of the invention, the motor is an electric motorand density FD of the fluid is estimated by current flowing to theelectric motor. In another particular embodiment of the invention, thedrive shaft further comprises a variable distance element, the computerprogram further includes but is not limited to instructions to adjustthe variable distance element from a first distance value RD1 for thespace between the rotor elements to a distance value RD2 for the spacebetween the rotor elements based on a density FD of the fluid.

In another particular embodiment of the invention, the drive shaftfurther comprises a variable distance element, the computer programfurther comprising instructions to adjust the variable distance elementfrom a first distance value RD1 for the space between the rotor elementsto a distance value RD2 for the space between the rotor elements basedon a density FD of the fluid.

Although the programs and other various systems, components andfunctionalities described herein may be embodied in software or codeexecuted by general purpose hardware as discussed above, as analternative the same may also be embodied in dedicated hardware or acombination of software/general purpose hardware and dedicated hardware.If embodied in dedicated hardware, each can be implemented as a circuitor state machine that employs any one of or a combination of a number oftechnologies. These technologies may include, but are not limited to,discrete logic circuits having logic gates for implementing variouslogic functions upon an application of one or more data signals,application specific integrated circuits (ASICs) having appropriatelogic gates, field-programmable gate arrays (FPGAs), or othercomponents. Such technologies are generally well known by those skilledin the art and, consequently, are not described in detail herein.

Flowcharts and Block Diagrams of FIG. 1 show the functionality andoperation of various specific embodiments of certain aspects of thepresent inventions. If embodied in software, each block may represent amodule, segment, or portion of code that comprises program instructionsto implement the specified logical function(s). The program instructionsmay be embodied in the form of source code that comprises human-readablestatements written in a programming language or machine code thatcomprises numerical instructions recognizable by a suitable executionsystem such as a Turbomachine processor in a computer system or othersystem. The machine code may be converted from the source code, etc. Ifembodied in hardware, each block may represent a circuit or a number ofinterconnected circuits to implement the specified logical function(s).

Although the flowchart and block diagram of FIG. 1 show a specific orderof execution, it is understood that the order of execution may differfrom that Which is depicted. For example, the order of execution of twoor more blocks may be scrambled relative to the order shown. Also, twoor more blocks shown in succession in FIG. 1 may be executedconcurrently or with partial concurrence. Further, in some embodiments,one or more of the blocks shown in FIG. 1 may be skipped or omitted. Inaddition, any number of counters, state variables, warning semaphores,or messages might be added to the logical flow described herein, forpurposes of enhanced utility, accounting, performance measurement, orproviding troubleshooting aids. It is understood that all suchvariations are within the scope of the present inventions.

Any logic or application described herein that comprises software orcode can be embodied in any non-transitory computer-readable medium,such as computer-readable medium, for use by or in connection with aninstruction execution system such as, for example, a Turbomachineprocessor in a computer system or other system. In this sense, the logicmay comprise, for example, statements including instructions anddeclarations that can be fetched from the computer-readable medium andexecuted by the instruction execution system. In the context of thepresent inventions, “computer-readable medium” may include any mediumthat may contain, store, or maintain the logic or application describedherein for use by or in connection with the instruction executionsystem.

The computer-readable medium may comprise any one of many physical mediasuch as, for example, magnetic, optical, or semiconductor media. Morespecific examples of a suitable computer-readable medium would include,but are not limited to, magnetic tapes, magnetic floppy diskettes,magnetic hard drives, memory cards, solid-state drives, USE flashdrives, or optical discs. Also, the computer-readable medium may be arandom access memory (RAM) including, for example, static random accessmemory (SRAM) and dynamic random access memory (DRAM), or magneticrandom access memory (MRAM). In addition, the computer-readable mediummay be a read-only memory (ROM), a programmable read-only memory (PROM),an erasable programmable read-only memory (EPROM), an electricallyerasable programmable read-only memory (EEPROM), or other type of memorydevice.

The Turbomachine processor may further include a network interfacecoupled to the bus and in communication with the network. The networkinterface may be configured to allow data to be exchanged betweencomputer and other devices attached to the network or any other networkor between nodes of any computer system or the video system. In additionto the above description of the network, it may in various embodimentsinclude one or more networks including but not limited to Local AreaNetworks (LANs) (e.g., an Ethernet or corporate network), Wide AreaNetworks (WANs) (e.g., the Internet), wireless data networks, some otherelectronic data network, or some combination thereof. In variousembodiments, the network interface 159 may support communication viawired or wireless general data networks, such as any suitable type ofEthernet network, for example; via telecommunications/telephony networkssuch as analog voice networks or digital fiber communications networks;via storage area networks such as Fiber Channel SANs, or via any othersuitable type of network and/or protocol.

The Turbomachine processor may also include an input/output interfacecoupled to the bus and also coupled to one or more input/output devices,such as a display, a touchscreen, a mouse or other cursor controldevice, and/or a keyboard. In certain specific embodiments, furtherexamples of input/output devices may include one or more displayterminals, keypads, touchpads, scanning devices, voice or opticalrecognition devices, or any other devices suitable for entering oraccessing data by one or more computers. Multiple input/output devicesmay be present with respect to a computer or may be distributed onvarious nodes of computer system, the system and/or any of the viewingor other devices shown in FIG. 1. In some embodiments, similarinput/output devices may be separate from the Turbomachine processor andmay interact with the Turbomachine processor or one or more nodes ofcomputer system through a wired or wireless connection, such as throughthe network interface.

It is to be understood that the inventions disclosed herein are notlimited to the exact details of construction, operation, exact materialsor embodiments shown and described. Although specific embodiments of theinventions have been described, various modifications, alterations,alternative constructions, and equivalents are also encompassed withinthe scope of the inventions. Although the present inventions may havebeen described using a particular series of steps, it should be apparentto those skilled in the art that the scope of the present inventions isnot limited to the described series of steps. The specification anddrawings are, accordingly, to be regarded in an illustrative rather thana restrictive sense. It will be evident that additions, subtractions,deletions, and other modifications and changes may be made thereuntowithout departing from the broader spirit and scope of the inventions asset forth in the claims set forth below. Accordingly, the inventions aretherefore to be limited only by the scope of the appended claims. Noneof the claim language should be interpreted pursuant to 35 U.S.C. 112(f)unless the word “means” is recited in any of the claim language, andthen only with respect to any recited “means” limitation.

The invention claimed is:
 1. An apparatus comprising: a first rotarymachine operable for transformation of energy between rotary mechanicalenergy and fluid kinetic energy, the rotary machine comprising: a driveshaft; a tubular housing defining a fluid input and a fluid output and arotor operating region; a rotor mounted within the rotor operatingregion for rotation about a rotor axis of rotation through the driveshaft, the rotor comprising a first rotor end and a second rotor end,the axis of rotation extending between the first rotor end and thesecond rotor end, the rotor operating region being positioned betweenthe fluid input and the fluid output; and a plurality of rotor elementsfor the rotor, the plurality of rotor elements being axially spaced fromeach other along the rotor, the plurality of rotor elements comprising aplurality of surfaces oriented on the rotor so as to be concentric tothe rotor axis of rotation, the plurality of rotor elements axiallyspaced a distance RD between the rotor elements, defining therebetween aplurality of radial flow paths each having a path width PW defined bythe distance RD between the rotor elements, the plurality of rotorelements defining a plurality of centrally positioned apertures thatcollectively define an unrestricted interior opening that surrounds thedrive shaft and connects to the plurality of radial flow paths to permitradially outwardly fluid flow through the plurality of radial flowpaths, the unrestricted interior opening receiving fluid flow from thefluid input to provide the radially outwardly fluid flow through theplurality of radial flow paths; a solids port through which the solidsare removed from the fluid; wherein the drive shaft further comprises avariable distance element, a computer program further comprising:instructions to adjust the variable distance element from a firstdistance value RD1 for the space between the rotor elements to adistance value RD2 for the space between the rotor elements based on adensity FD of the fluid wherein the space is inversely proportional tothe FD.